Tank washing apparatus



Aug. 2, 1960 L. v. LlONE TANK WASHING APPARATUS 5 Sheets-Sheet 1 Filed Aug. 1. 1958 Inventor Leonard V. Lione 1 0 L. v. LIONE 2,947,482

TANK WASHING APPARATUS Filed Aug. 1, 1958 5 Sheets-Sheet 2 Leonard V. Lione Inventor Aug. 2, 1960 Filed Aug. 1, 1958 L. V. LIONE TANK WASHING APPARATUS 5 Sheets-Sheet 3 78 17 8lb 89 770 62 88b 76c 63 620 I8 64 Bio l4 g 32 3lb Leonard V. Lione Inventor Aug. 2, 1960 L. v. LIONE TANK WASHING APPARATUS 5 Sheets-Sheet 4 Filed Aug. 1, 1958 Leona rd V. Lione BY CLQQAflorney Aug. 2, 1960 L. v. HOME 2,947,482

TANK WASHING APPARATUS Filed Aug. 1, 1958 5 Sheets-Sheet 5 Leonard V. Lione Inventor By \Q.QMWftorney Patented Aug. 2, 1960 TANK WASHING APPARATUS Leonard V. Lione, Fanwood, N.J., assignor to Butterworth System, Inc., a corporation of Delaware Filed Aug. 1, 1958, Ser. No. 752,510

7 Claims. (Cl. 239-227) The present invention relates to an apparatus particularly adapted for cleaning the interior wall surfaces of a container vessel. More particularly, the invention relates to a tank washing apparatus providing for the discharge of high pressure jet streams of a cleaning liquid so as to impinge against the interior wall surfaces of such container vessel. The invention further relates to a tank washing apparatus assembly including reaction jet nozzle drive means whereby the assembly is rotated about a primary assembly support axis by rotation of the nozzle drive means about a secondary axis perpendicular thereto, and also including means for selectively governing the speed of rotation of the assembly and of the nozzle drive. More specifically, the invention relates to a tank washing apparatus assembly, providing means. for simultaneous rotation of elements thereof about right angularly related axes, and including a pump means actuated by such rotation to govern the speed thereof. In addition, the invention relates to the drive and governor means as incorporated in the complete apparatus assembly.

In conventional tank washing apparatus of the character contemplated, a nozzle structure is mounted on a vertically suspended housing for rotation about a horizontal axis, while the housing is rotated about a vertical axis. conventionally, also, the housing contains a water motor, or impeller, driving speed reduction gears for rotation of the nozzle and housing. In some devices, the gears and other parts of the driving means are contained within the housing, while in most such devices the operating parts and gears are mounted externally, and/or supported in bearings having large clearances to provide for lubrication and/or cooling by water or other cleaning liquids escaping therethrough.

In the first mentioned apparatus design difficulties are encountered in the original manufacture and assembly of the apparatus. In order to maintain a lubricated drive means and gear box, eifective seals must be established, and leakage of the cleaning liquid effectively limited. These requirements are difiicultto attain in the limited space available. They are also complicated by the fact that cleaning liquid pressures above 150 psig may be attained in the flow passages through the housing.

In the second design form, the exposed mechanisms and gearing are most liable to damage. Also, because of the loosely fitted operating parts, at even moderate pressures leakage is so excessive that effectiveness of the nozzle streams is considerably reduced.

It is an object of the present invention to provide a cleaning device of relatively simple construction and assembly whereby to accomplish the desired effective results without the deficiencies inherent in the devices known from the prior art. It is a further object of the invention to provide such an apparatus wherein all parts requiring lubrication are contained so as most effectively to avoid access of cleaning liquid thereto. Also, it is an object oftthe invention to provide a structure which is a unitized assembly of a series of separable sub-assembly units whereby to facilitate initial construction and subsequent service or repair. Additionally, it is an object of the invention to provide means for rotating the entire device about a first axis while rotating a nozzle structure, included in said device, about a second axis related per-' pendicularly to said first axis, wherein said rotational means includes a governor for control of the speed of rotation of said nozzle and said device.

The invention and its objects may be more fully understood from the following description, especially when it is read in conjunction with the accompanying drawings, of which:

Fig. 1 is a view in elevation from the nominal front of the apparatus with parts broken away or removed to show certain essential features of construction contemplated according to the invention;

Fig. =2 is a plan view looking down on the apparatus as illustrated in Fig. 1;

Fig. 3 is a view of the apparatus in vertical section, with parts broken away and in elevation, taken along the line III-IH of Fig. 2;

Fig. 4 is a view in horizontal section taken along the line IV-IV of Fig. 3 with parts shown in elevation;

Fig. 5 is an exploded view of a portion of the discharge nozzle structure as shown in Fig. 3, taken substantially along the line VV of Fig. 1 and including the overriding clutch and driving means therefor;

Fig. 6 is a vertical section, through the gear case :1, taken along the line VI-VI of Fig. 4;

Fig. 7 is a view in horizontal section, similar to that taken along the line IV-IV of Fig. 3, to illustrate an alternate form of internal construction in the gear case 1; and

Fig. 8 is a vertical section, through the gear case 1, taken along the line VIII-VIII of Fig. 7.

In the drawings, like parts are designated by the same numerals. Accordingly, the several figures will be referred to specifically by number only as required to identify parts as shown in specific figures.

As shown, the apparatus is composed of a series of sub-assembly units including a gear case 1, a liquid delivery head and nozzle structure support: and delivery head unit 2, a combined housing cap, support tube, and coupling unit 3, and a nozzle structure 4. Also as shown, the units 1, 2, and 3 are provided so as to be joined in superposed ascending order along a common axis and in spaced relation longitudinally thereof.

The gear case unit 1, as shown, is shaped to provide vertical side wall portions 11 of substantially horseshoe shape, wherein the ends, or quarters are connected by a flat vertical cross wall portion 12 at the front of the case. The upper end, or top wall 13, matches the side wall peripheral conformation and is integral with such wall portions. The upper surface of the gear case unit is stepped upwardly from the fiat wall portion 12 in two steps. Primarily, this is to provide a maximum spacing between it and the bottom wall portion 45 of the delivery head 2 next above in the complete assembly, and also to conform to the shape of such bottom wall.

An integral, enlarged and platformed boss 14 is provided to extend upwardly from the top wall, extending across a portion of the arch or toe of the shaped side wall 11. A series of additional and individual bosses 15 are disposed in spaced relation along the peripheral edge of the top wall portion 13 from each end of the platformed boss 14, toward the juncture of the top wall with the cross wall 12. Thus, these bosses provide an enclosure open at the cross wall end. In addition, each boss 15 terminates at its upper end in a planecommon to that of said platformed boss, and further is drilled and tapped.

The top end wall 13 of the gear case 1 further provides guide and stop means for proper location of the unit 2 next above. In the unit as shown, the guides take the form of two oppositely disposed smaller bosses 16 and 17 inwardly of the peripheral bosses 15. Each of the bosses 16 and'17 is shouldered to provide curvilinear, inwardly facing vertical wall portions 16a and 17a respectively. The inner side of the boss 14 is similarly shouldered at 18, and on substantially the same radius which is centered on the axis of the delivery head 2. The function and depth of the shouldered portions 16a, 17a, and 18 are as later described.

Interiorly, the gear case 1 is provided to house a drive transmission and governor system. As, shown in the drawings, a boss 26, on the outer surface of' cross wall; 12, defines a passageway adapted to receive a combined shaft seal, bearing retainer and bearing 27 for'the shaft 25 adjacent its outer end. The inner end of the shaft 25 is supported by a suitable bearing in the case wall portion 11. This end of the shaft 25 carries a bevel or miter gear 28, while the outer end extends through the element 27 to receive a spur gear pinion 29.

A vertical shaft 31 is supported in a passageway 14a defined in the boss 14, and by means of a bearing and retainer seal assembly 32 adapted for threaded engagement in the passageway. The upper surface of the retainer seal is disposed substantially flush with the surface of the boss, and the upper end of the shaft flush with the retainer surface. This end'of the shaft is provided with a threaded recess 31a, adapted to receive the threaded end of another shaft section as later set forth. The shaft 31 is disposed so that its axis is in right angular intersecting relation to the axis of the shaft 25. A shouldered'portion 31b suspends the shaft 31 on the bearings therefor. The lower end of the shaft carries a miter gear 33 for meshed relation with the 'gear 28 on shaft 25. The lower end of the case 1 is moulded to a substantially circular contour and is provided with a re movable sealed cover plate 34. i

As illustrated by Figs. 1 and 3, the nozzle support and delivery head unit 2 is next in the ascending order of the assembled units. This unit has a conformation substantially corresponding to that ofthe gear case 1, including horseshoe shaped side wall portions 42, and a flat cross wall portion 43. Top and bottom end'wall'portions44 and 45, respectively,'are formed integrally'with the side wall and cross wall portions, and are flanged outwardly from the side wall portions of the case as indicated by numerals 2a and 2b in Fig. 1. The bottonrend wall flange 2a is adapted to be seated on the bosses 14 and 15 of the case and to be attached'thereto asby the bolts shown. The upper end wall flange 2b is" adapted to receive and be bolted to the lower end of the housing cap of unit 3.

The cross wall 43 is of substantially circular, peripheral contour, extending radially beyond the side wall and bottom endv wall portions 42 and 45. Integral with the cross wall 43 is annular peripheral rim wall 46 extending outward therefrom at right angles to the surface, and a concentric axle tube 47, which extends outwardly beyond the rim. Between them, the rim wall 46 and the axle tube 47 define an annular recess with the external surface of the cross-wall 43 forming the bottom thereof. In a lowersector of the cross wall 43, and displaced from a diameter thereof which is parallel to the assembly axis, the rim is thickened to provide a radial extension porrtion 46a. This portion defines a chamber having a central axis lying substantially in a' circular line common to the major portion of the outer periphery of the rim wall 46. I The chamber is of circular contour, opening through the'internal surface of the wall 43, and adapted to receive the outer end of the gear case shaft 25 and the attached spur gear 29. As shown, the extension 46a is, also located so as to match the location of the shaft 25 and gear 29 and to be concentric therewith. Means areprov-ide'd to se'al the boss 26 in the opening through the wall.

4 43 and the rim extension portion 46a. The chamber, by reason of its disposition also opens into the recess between the wall 43 and the axle tube 47. Spider vane portions 47a in the outer end of the tube 47 support a projecting flow diffuser element 48, and a nozzle support stub shaft and bearing 49.

As shown, the bottorn'wall 45 of the delivery head 2 inclines downwardly at 45a. to join the reverse surface of cross wall 43 substanti'allyat."level corresponding with the juncture of the lower halfofthe. axle tube 47--with the obversefo'r external. surface of cross wall 43. The case 2 definesan interior, substantially L-shaped, delivery passage 41 which opens at the upper-end through the upper end wall portion 44by way of-anjintegral axial tubular portion 44a, and at the lower end through the cross wall 43, and the axle tube 47.

A portion 42a of the nozzle support and delivery head side wally42, opposite to the extension portion'46a of the cross wall 43, is enlarged drilled longitudinally to form a shaftway 42b. This shaftway-has amaxisin right angllar intersection relation to' theaxis ofth'eichamber in the extension portion 46a, and tothe axis oftgearcase shaft 25. A shaft 62. disposed in this shaftway extends downwardly therethrough. Thei'lower end 62a of: the shaft is threaded for connection. in the threaded recess in the u'pperendof gear case shaft3 1, to be driven thereby. The shaft 62' is elongated, and theupper end' 62b extends upwardly beyond the shaftway'and extension portion42a. The shaft carries a spur gear 63atits upper end; and also is provided with a screwdriver receiving slotted: portion 620 therein. Referring again to the bottom wall '45, as seenin. Figs. 1. and 3, it is, to be noted that the lower or outer face is milled about the periphery common to" the flanged 'portion 2a thereof, and'along a contour substantially conforming to'that'of the side wall portions 42, whereby to produce an angular, shouldered peripheral recessed per tion 64, having an inner vertical walld'epthslightly less than the shouldered portions 16a, 17a and 18 ,provided'in' the bosses 16, 17, and 14, respectively, and aradius'of curvature substantially equal tothat of the shouldered portions 16a, 17a, and 18. With the'flange 2a in contact with the upper ends of the bosses 15'and'14, then the recessed Wall 64 is engaged by' the wall portions 16a and 17a to guide the case 2 into alignment with the case 1, with bolt holes in the flange 2a aligned with those in the bosses 15 and 14, the shoulder o'f'recess portion 64 being finally engaged by the-shoulder-wall 18" acting a's-a stop therefor.

In the unit 3, the numeral 71 designatesa supportand cleaning liquid inlet tube having "arrenlarged lower end 72, internally and externally shouldered as at 73", and at 74 and 75 respectively, and defining an internal passage way 76c flared at its inner end to match the. passageway 41 at the inner periphery of theannular shoulder 73'. The tube 71 is sealed 'in rotative relationto the axial tubular portion 44a of the delivery head top wall'44, by means of theannu1arseal'ring'44b inounted and disposed asshownp In the structure illustrated, the external shouldered portions 74 and 75-respectivelyprovide mounting surfaces for an externally toothed ring gear 76, and the inner race 77 and rollers 77a of a two part conical roller-bearing. The other conical raceway portion otthe bearing is 'indicated' by the'numeral 78; Thering gear-76 is-re'tained against longitudinal movement on the tube 71 by means of a spring retainer ring 7 9,and'agai11st *r'otationby means .5 for the upper end of the tube '71, which, as shown, is adapted to extend through such passageway in sealed, rotative relation to the walls thereof. The numeral 8-2 designates the annular seal means. Internally the cap 81 is annularly shouldered as at 84 and 85 substantially to match the external shoulders 74 and 75 of the tube 71, and in such fashion as to provide a chambered portion 81b adapted to be packed with a lubricant material. The cap 81 completely encloses the enlarged, lower portion of the tube 71 in rotative surface relation, and the respective wall surface portions are sealed as by the seal ring 80. The shouldered portion 85 in the cap 81 is adapted to receive the conical bearing raceway 78 in press fitted relation. Bosses such as indicated at 86 and 87 peripherally of the rim of the inverted cup-shaped housing 81 are disposed and adapted to be received by the flange 2b in aligned relation to bolt holes therein for rigid connection of the case thereto. The bosses such as 86 and 87, extend beyond the housing rim, whereby to provide spaced separation of the housing 81 from the flange 2b.

Integral with the outer wall of the housing 81 there is formed a thickened radial extension 88. This extension portion is drilled on an axis parallel to the central axis of the housing, and the assembly, to provide a shaftway 88a to receive the upper end 62b of the shaft 62, and a chambered portion 88b at the upper end of the shaftway. This chambered portion opens through the inner wall of the housing into the chambered portion 81b, and is adapted to receive the spur gear 63 on the upper end of the shaft 62. The disposition of the chamber and the dimensions of the ring gear 76 and spur gear 63 are such as to provide for engagement between the gears. A threaded cap 89 provides a closure for the upper end of the shaftway 88a and chamber 881).

Included in the subassembly 3 is a means for coupling the apparatus to a source of cleaning liquid, such as a hose or pipe, not shown. This means is composed of a collar 91 and a male coupling element 92 exteriorly threaded for engagement by a coupling nut on a hose or pipe connection. The collar 91 and element 92 are joined by means such as bolts 920. The collar 91 is freely fitted on the upper end of the tube 71, as is also the element 92. Each of the collar 91 and element 92 is formed with an annular shouldered portion, 91a and 92a respectively, disposed for opposite facing relation when assembled on the tube 71, and the coupling element 92 is provided with an annular seal ring 92b to engage the outermost end of the tube 71.

The face of the shoulder 91a on collar 91 is provided with a series of notched portions 93 forming a corresponding series of teeth 94, wherein the tooth and notch side wall portions 95 are inclined at an angle of between about 15 and about 75 to the clearance line of the teeth. The collar thus forms the primary element of an overriding clutch, wherein the secondary clutch element is an inwardly flanged annulus 96 adapted for threaded engagement with the upper end of the tube 71 between the shouldered portions 91a and 92a, and maintained in such engagement by a retainer ring 97'. The lower edge of the annulus 96 is notched and toothed .to match the upper surface of the shoulder 91a, the notch and tooth portions being designated by the numerals 98 and 99 respectively, and the inclined side wall portions by the numeral 100'. The shouldered portions 91a and 92a are spaced at a distwice at least. equal to the assembled distance between the'surface of a tooth portion 99 and the upper surface of ring 97, plus the depth of a notch portion 93, whereby the crown surfaces of tooth portions 94 and 99 may be disposed substantially in a common plane.

The remaining sub-assembly unit is the nozzle structure 4. Basically, the nozzle structure 4 is composed of an annular hub 101 having annular shouldered portion 102, wherein said hub is adapted for telescopic, journalled fit over the axle tube 47-. Integral with the hub 101 are at least two nozzle portions 103 and 104 which, with the hub 101, form a substantially offset T discharge conduit means wherein the arms of the T are the nozzle portions 103 and 104 disposed in substantially perpendicular radially displaced relation to the axis of the nozzle hub 101. A recessed portion 101a internally of the hub is adapted to be received in sealed rotative relation to the flow diffuser element 48 and to be axially engaged by the outer end of the stub shaft 49, through an axially defined shouldered passage 101b in the hub. A cap 105 provides for threaded engagement with the threaded end of the shaft 49, and maintains the mounted relationship of the nozzle structure to the axial supports therefor. Set screws 105a prevent loosening of the cap 105.

A series of annular seals, including seals such as indicated by the numerals 106, 106a and 107 are provided against liquid leakage from or into the related rotative joints. Also, where such seal is intended to hold against a positive pressure of liquid, as are the seals 106 and 106a, provision is made to release such pressure intermediate the seal and the joint protected. Thus, in the nozzle structure 4, the face of the hub portion is provided with a serie's of passageways 108 defined therein so as to communicate with the joint between the nozzle and the axial diffuser portion 48 intermediate the seals 106 and 106a which protect the bearing 109. Additionally, to seal against the pressure of cleaning liquid passing into and through the nozzle structure 4, the axle tube 47 is provided with a pair of annular groove portions spaced longitudinally of the tube at the outer end thereof and adapted to receive seals 110 and 111. To relieve the pressure of liquid passing the first seal 110, and to discharge any such leakage, the hub 101 is provided with an annular groove portion 112 disposed so as to lie between the seals. Radial passageways 113, also defined in the hub 101, communicate between the groove portion 112 and the ambient atmosphere.

As shown in Fig. 3, when the hub 10 1 is mounted on the axle tube 47, the annular shouldered portion 102, with the rim 46 and cross wall 43 define an encased chamber inwhich the outer wall surface of the hub portion 102 is opposed to the inner wall surface of the rim 46, and the hub shoulder of the portion 102 is opposed to the cross wall 43. Also as shown, the shoulder portion defines an annular recess 114 paralleling, and intermediate the outer and inner wall surfaces of the hub. The

outer edge of this recess defines a plurality of peripherally spaced slots 115, extending through the face of the shoulder, and a plurality of passageways 116, defined in the hub 101, communicate between the bottom of the recess and the interior of the nozzle structure within the hub, and at the roots of the nozzles 103 and 104.

Within the recess 114 is disposed an annular seal member 117 of a resilient, deformable material, such as an 0 ring of rubber or a synthetic material. Also disposed in the recess 114 toward the outer end thereof is an annular overriding clutch plate 118 provided with a plurality of ear portions 118a adapted to fit the slots in the face of shouldered portion 102, and equal in number to the number of such slots. Each ear portion 118a is under cut to permit a portion of the plate to enter the recess below the bottom of the slots, and to provide clearance for reciprocal movement of the ears and plate within the depth of the slots.

The outer face of the clutch plate 118 is provided with a series of tooth and notch portions respectively disposed in alternate sequence circumferentially of the plate face. Each notch has a depth substantially equal to the height of adjoining tooth portions, and the tooth wall or face connecting between the crown of a tooth and the bottom of a notch is angled toward the notch center. Preferably the tooth face angle is form about 15 to about 75 to the clearance line. The total depth of each tooth and each notch is preferably substantially equal to the depth of the plate under cut portion, and the total thickness of the plate,..including the. tdothportions, is substantially equalto the depth of.theslots 115.... Next in sequence from the. faceoffshoiilderportion 102 towardthe inner.end of the hub1101, is .an annular. gear r 121, havingguperipheral. gear .teeth matchedto the spur gear. pinion 29,. and adaptedtofb'edisposed for rotation on the.hub,while..engaged.by said spur.gear.. The. outer face of the gear 121 provides a series of notch and .tooth portions similar andequaliin number to. those provided by the plate .118, buthaving a slightlylgreateroverrall depth and height. These notchand tooth portions are disposed .along the outer faceof. the annular gear, have a width about equal to therecess 114. and .a clearance line lyingin the outerface of-thesgear, which butts. against the shoulder face portion. The gear is retained against the shoulderface, byfla spring steel retainer ring 1.24 fitting againstthe face ofQa recessed portion on theinner side or face of the gear and engaged at itsinner periphery in an annular; groovein the wall'of the hub'portion 102.

In addition to the transmission drive-provided in the case 1 by the spur gear 29,..through shaft 25, bevel gears 28 andv 3'3, and the stub shaftv 31, the case 1' also houses means for governing the speed .of rotation of th'e shaft 25, and therebythe speed of rotation of the nozzle, and of theentire assembly about their respective axes. One suchmeans in its structural relationship to the transmission drive and casefisillustrated by Figs. -3, 4 and 6. An alternate form of governor means is illustrated by Figs. 7 and 8. a

As shown in Figs.l3, 4 and 6, the governor comprises a reciprocating pump having variable area inlet and outlet passages on ports. In these drawings, the numerals 19 and 20 designate a pair of laterally spaced lugs formed in and extending perpendicularly from theinner surface of the cover plate 34. These lugs are drilled at their outer ends on a common axis, parallel to the axis of the shaft 25, to 'rec eiveho ppo'site ends of a shaft 21. The numerals 22 andf23 designate a pair of laterally'spaced standards alsoforrned'in and extending perpendicularly from. the inner surface of the cover plate 34. The

standards 22and. 23. alsoare drilled at their outer ends on a common .axis parallel to theshaft 25, and are adapted to receive bearings. 22a and 23a respectively for a shaft 24.. The shaft 24 is adapted to receive a spur .gear. 30. mounted thereon so as to be disposed intermediate the standards .22 and 23. This ssh-affincludes an. .integralcrank portion 24a outwardly of the standard 22. The shaft 24 is driven for rotation through the spur gear 30..by;means of a spur'gear mounted on the shaft 25. nextadjacent'to the bevel gear-28. I

Mounted on theshaft21isacylinder block 36, drilled laterally at onev end.36a to receive the shaft; and longitudinally to provide'portsor passageways 36b. and 36c.

A bore drilledthrough theop posite end of the block provides a cylinder chamber 37. The-ports 36b and 360 communicate between the chamber 37 and the interior of the case .1.. Each of the ports 36b and 360 is provided with a valve plug, such as. indicated by the plug 38 for the port36b, which is adapted for threaded movement in theblock 36ft) alter the cross-sectional area of the port. Preferably the ports 36b and 36c are of different diameter,..whereby..to provide greater flexibility of adjustment by the valve plugs. .An access port and threaded plug 34a therefor provide means whereby the valve plugs and may be adjusted as required.

Cooperating with the cylinder block 36 to provide the contemplated governor pump is a combined piston and piston rod, operatively connected to the crank 2 4a. In the, drawings, the. numeral 39 designates a piston head provided for insertion in. the cylinderdrawing 37. As shown. the head is sealed therein by means of. a seal ring Attached to the outer end of the head, in substantially integral relation sthereto is a piston,.rod..40.

the crank 24a in a journalled bearing as shown. Rotafl'heflouterlendof the..r.od,.,=40uisv drilled to, accommodate 'pump. Such. adjustment ordischaige c ntrol' 8 tion of thev shaft 24,, and crank 214a moves the head and rodreciprocally inthe cylinder chamber,37', the throw ofthe crank being accommodated bypscillatory-pivotal movementof the cylinder blockro'nuthe shafLZl. The case 1 being adaptedflto contain a liquid lubricant,.outward movement of jthe piston byjth e jcranl and rod produces a suction strokewhich causej s liqj11id'to, flow hrpugh one or both ports into the chamber 37. Inward movement of the pistons produces a'cornpression. stroke which then forces liquid outwardly into; the casing 1.

.Qneach of, the suction and compression strokes the .restr qn p de y the. ports 36band .3 0 exe ts a br k n ac o on ro a of the crank 24a a d 1s.h .f. .2..

and 8. In this form, the reciprocating pump is replaced by a vane pump 50 having an upper wall portion Stla adapted forjfitted engagement with the inner surface of the gear case upper wall 13; opposite outer and inner end wall portions 51 and 52 respectively; and a bottom wall 53.- The bottom wall is formed with an enlarged or thickened portion 53a. Defined within the pumpx5fl is a cylindrical chamber 501), disposed so. that with the wall StIa'engagedwith the casing wall 13, theaxisof the chamber is parallel with the axis of the shaft; 25 but in a horizontal plane displaced-vertically from one oom- 1non to the axis of shaft 25. Ihe end wall 51 formsa hollow boss 51a adapted to be received in a recess sfia formed in the inner face of a'plug 54, disposed in threaded engagement with an access port in thewall gear c ase '1,- .whilethe; end wall 52 defines a shaftway or passage 52a All of these elements, including the boss51a, recess .54a, .plug 54, and shaftway 52a are disposed on an axis Whichlies in jja horizontal plane common to the axis of the shaft 25 and a vertical plane common to. the axis of chamber 5tib.

A shaft55 is disposed inthe case 1,,.iniai11 wit11 the shaft 25 and with its axis in thesame horizontal plane. The axis of the shaft 55 also lies iniavertical plane common to that of the chamherISBb, recess 54a and shaftway 52a, One end of the shaft 55'is adapted for support in a bearing 51b, in the boss 5121. The

disposed end of the shaft is supported in a bearin I .lIh

in a receiving recess 1a in the gear ,cas wall. '1

shaftway SZaprovides for-passage of the shaft 55 throiigh the chamber 50b I Within the" chamber 50b, 21 typical pun'ip' refer; mounted in concentric relation to the] shaft 55 a eccentric relation to the chamber. Also as. shown; vanes 57, 58, 5 9 and 60"are providedQfor r 1 movement in rotor slots,5 6a, 56b 56c, and 56d" esp tively, with compression spring elements 57a and and b, 59a and b, and 60zz and b, s'et in rc the bottom wall of each slot serving toima several vanes in operative contact. with 'he .c tuber inner wall. The shaft 55 is driven are ns Qof meshing spur gears 55 1 and 2511 mounted;respectively o e shafts 55 and 25. Inlet and outlet ports com 131 between the pump chamber are designated in Figs. 8 by the numerals 61a and'6 1b, respehtively. .Qil'ef'br more such inletland outletports may be .fe'niployed If more thanone outlet port. is employed, preferably h port will have adiiferentfdiameter, i n orderto pro maximum adjustment of discharge 'haraete'ristiesg i by means such as the valve plug dlfadaptedi. ceived in a threaded bore therefor in thellexten on Ira-W or ports 61b.

to alter the cross-sectional area of the port In assembling the apparatus according to the present invention, a particular feature of the invention is emphasized. This feature involves the separability and replaceability of the sub-assembly comprising the gear case 1.

This unit provides the first unit in the assembly procedure, and is preferably placed on a flat surface, or held in a vise, with the boss 14 uppermost. In this position the delivery head flange 2a is applied to the bosses 15 at the forward portion of the side wall 11 and substantially at the ends of the gear case cross wall 12, and slid over the remaining bosses 15 to the outer periphery of the boss 14. During such movement, the recessed portion 64 will first engage the vertical walls of the shouldered portions 16a and 17a, in the bosses 16 and 17 respectively. When the recessed portion 64 abuts against the wall of shoulder 18, the impeller case will be positioned with the spur gear 29 in the chamber provided therefor in the portion 46a, and with the shaftway in the portion 42a substantially centered on the threaded end of the shaft 31. As thus positioned, the flange 2a is bolted to the bosses 15 and 14.

Next, the tube 71 is applied over the tubular inlet portion 44a, the shoulder 73 engaging the upper end of the tubular portion 44a, With the tube 71 in place, the housing cap 81 is applied over the tube so as to align the peripheral and extended boss portions of the cap, such as designated by the numerals 86 and 87, with the corresponding bolt holes in the flange 2b of the case 2. The cap is then fastened to the flange 2b, substantially in the manner shown, by bolts such as 86a and 87a. By reason of the predetermined location of the radial extension 88, this part is now located so as to align its defined shaftway 88a with the shaft way 421) defined in the portion 42a of impeller case 2. Before mounting the housing cap 81, of course, the seals 80 and 82 have been properly applied in their receiving groove portions shown, and the ring gear 76 and bearing parts 77 and 78 have also been applied in the relationships shown and described.

Now the shaft 62 is inserted in the shaftway 88a, and through that part 4217 which is defined in the portion 42a of the delivery head 42, into threaded engagement with the upper end of the shaft 31 in gear case 1. Engagement of the shafts 62 and 31 is accomplished by means of a screwdriver, of which the blade is inserted in the slot portion 62c. As the shaft 62 is thus engaged, the gear 63 becomes engaged with the gear 76. Continued rotation of the shaft 62 rotates the tube 71, until the shaft is completely seated. The threaded cap 89 is then inserted to seal the chamber 88b.

The collar 91 is now slip fitted over the upper end of the tube 71 which extends through the upper end of the housing cap 81. The annulus 96 is then threaded on the tube with the internal annulus flange engaging a shoulder on the tube as shown, and the retainer ring 97 is applied. As previously noted, with the collar 91 at rest on the upper end of the cap 81, the crowns of the teeth 94 formed in the collar flange 91a should be in substantially co-planar relation to the crowns of the teeth 99 on the lower end of the annulus 96. The male coupling 92 is now slip fitted over the end of the tube 71, and bolted to the collar 91, to complete the main part of the assembly.

At this time, the nozzle structure may be prepared for mounting on the axle tube 47. As a first step, the seals 106, 107, 110, and 111 may be positioned in the receiving grooves therefor. Next the O ring 117 is inserted in the recess 114, and the clutch plate 118 inserted over the ring 117 with the ears 118a disposed in the slots 115 and teeth 119 facing toward the inner end of the hub. The annular gear 21 is then applied, to the shouldered hub portion 102 with the teeth 122 facing the teeth 119 on plate 118, and the retainer ring 124 is fitted into the groove provided on the wall of shouldered portion 102.

As thus assembled, the nozzle structure 4 is pre aredfor mounting on the axle tube 47. This is done by aligning the peripheral teeth on the gear 121 with the teeth on the gear 29, and sliding the hub 101 over the axle tube 47, with the threaded end of the stub shaft 49 extended through the hub axial passageway 101b. The cap is then threaded on the shaft 49, and the set screws 105a tightened.

A particular feature of the apparatus provided by the unitized assembly described resides in the arrangements whereby the operating parts required to be lubricated are protected from access of a cleaning liquid passed through the discharge passageway and nozzles. As shown, each compartment of the assembly except the nozzle structure is a substantially self-contained unit, and, in the assembly is substantially separated from a next adjoining unit. Thus, with cleaning liquid employed at high pressures, the unit separation is utilized to prevent leakage from one unit from reaching another unit directly under the operating pressure. For example, a vulnerable area in most machines of the type contemplated is at the juncture between the liquid inlet and the delivery head, another is at the juncture between the gear enclosure and the delivery head. In the apparatus according to the present invention each of these junctures is pressure relieved by direct access to an ambient atmosphere at a lower pressure. Thus, the failure of the seals provided for high pressure zones does not automatically lead to contamination or damage in all adjoining zones. This feature is of special importance for the protection of such elements of the structure as the bearings and gears in the housing cap unit, the gear case unit, and the directly related nozzle drive.

Another particular feature of the apparatus is found in the provision for removal, replacement, or substitution of the drive gear sub-assembly as a unit. This may be accomplished by first rotating the collar and coupling 91 and 92 respectively to expose the cap 89 in extension portion 88, and then removing the cap to provide access to the upper end of the shaft section 62. With a screwdriver blade inserted in the slot 620, the shaft is unthreaded from its connection in the upper end of shaft 31, and lifted slightly in its shaftway to clear the boss 14. Now by sliding the assembled units 2, 3 and 4 forward over the bosses 15 and 14, these units may be separated from the gear case unit 1. A new or replacement gear case unit may be installed by reversing the procedure.

An additional feature of the invention is to be found in the simplified forms of the clutch mechanisms provided to permit manual rotation of the assembly about its longitudinal axis and of the nozzle structure about its rotational axis, without dismounting parts, and without damaging effects upon gears, shafts and bearings included in the drive transmission system. In the one instance the clutch arrangement is such as to be engaged by the suspended Weight of the assembly, plus the pressure of the cleaning liquid stream; in the other arrangement the clutch is engageable under the hydraulic pressure of the cleaning liquid stream as discharged from the nozzle structure.

In a typical cleaning operation, the assembly is prepared for use by connection to the discharge end of a high pressure hose or other conduit through the male coupling element 92. Usually such connection willbe made With the assembly in a horizontal or vertical position, whereby the clutch teeth 94 and notches 93 of the collar 91 are disengaged from the notches 98 and teeth 99 of the annulus 96. With the connection made, the assembly is inserted through any suitable opening or hatchway in the top wall of a container vessel, and preferably a hatchway disposed in more or less concentric relation with the walls to be cleaned or treated. This opening, because of the overriding clutch on the nozzle structure, need be only slightly larger than the greatest horizontal distance between the nozzle cap 105 and the tob, po jition' of the gear case sidewall 11. Should the nozzles "be extended toward the sides of the assembly, they may be rotated manually, through the nozzle structureioverriding clutch, so as to align them in substantially parallel relation to the longitudinal axis of the assembly.

When inserted within the tankand suspended therein, a cleaning or treating liquid is supplied through the suppl'yco'nduit connection undera pressure such as to discharge jetted streams thereof from the nozzles 103 and 104; "Preferably the machine is located so as to be not more than about twenty feet from a major portion of the container vessel interior wall surfaces. If greater distancesfare involved, the machine may have to be relocated in d'ifierent' areas of the vessel to accomplish proper contact of the jetted-streams with all portions of the wall surfaces. "Flow straightening means formed and/ or disposed in the discharge nozzles will aid in delivery of solid streams of liquid for impact against the wall surfaces :to be contacted thereby.

The liquid flowing through the inlet tube 71 passes outwardly through the delivery head passage 41, the axle. tube 47, and is discharged over the difiuser element 48 124. In this first engaging relationship, the teeth and:

notchesrin the plate 113 and gear 121 may or may not mesh.

However, reaction of the flow stream through the jet discharge nozzles 103 and 104 will rotate the nozzle 4 andplate 118 so that the teeth and notches are aligned with. those of the gear 121, and as the tooth and notch portions of the plate 118, and gear 121 come into meshingrelationship, the pressure on the O ring 117 forces plate 118 into meshed engagement with the gear 121'. Rotation of the plate in engagement with the gear 121 is transmittedby' the nozzle structure through the ears and slots118apand 115 respectively. So long as pressure is applied to the ring, the gear will be maintained in locked driving relation to the nozzle hub. When the liquid pressure on the 0 ring 117 is relieved, the clutch plate and gear faces do not disengage automatically, but when the nozzle is rotated manually, the plate 118 will beforcedinto the recess 114 as the teeth 119 rideover the angled wall portions of the teeth 123, along with the 0. ring 119.

Actuation 'of the gear 121. and pinion 29 drives the shaft 25 and also the shaft section 31, and through it the shaft section 62. As previously described, the gear 76 is fixed. in relation to the tube 71 by the tooth and recess, portions, 74a and 76a respectively. Also, the tube 71 is rigidly fixed 'by the weight of the assembly and thewater pressure to the Coupling 92 through the overriding clutch arrangement, the toothed collar and annulus members, and through the coupling to the connected supply. conduit means. Rotation of the shaft 62 and the attached gear 63, therefore, causes the gear 63 to wall: around the fixed gear 76 as a satellite while drawing the assembled portions including cases 1 and 2, and'housing cap 81 :along, with consequent rotation of the assembly about the tube 71 and the longitudinal axis. In the meantime, of course, 'the nozzle structure' is rotated about theaxle hub by the jet reaction pressure of the liquid discharged through nozzles 1113 and 164.

'Each' of the spur pinions 28 and 29 being attached to the same shaft 25, and'driven at the same speed, if both gears76and 121 had'the same number of teeth, nozzle an'di-assembly would rotate-at the same rate, 'andthe paths of the nozzle discharge streams would be constant, and would track. The object, however, is to provide constantly changing stream paths within the limits of chicient operation. It has been found that with a liquid pressure of between about to about 200 pounds, sufiicient impact force is obtained at a distance of about twenty feet f toproduce effective scouring dispersion of the streams, at the impact surface, and to obtain eifective cleaning action, if'the stream paths are separated by about one foot. This result is obtainable in sixty-three revolutions of the entire assembly if the gear 76 has sixty-four teeth and the gear 121 has sixty-three teeth.

With such a proportional relationship, for each revolution of the complete assembly about the longitudinal axis, the nozzle will make about 1.0158 revolutions about the radial axis provided by the axle tube 47. In other words, for every completed revolution of the assembly about the sixty-four tooth gear 76, the nozzle will make one revolution about the tube 47, plus a distance equivalent to one more tooth, since the gear 121 has only sixty three teeth. The difference as noted above is .015 8 revolution, or 5.71 (360+63) in the 360 periphery of each of the gears 76 and 121.

With the axis of the nozzle considered to be located in a horizontal plane the axis of each stream will 'describe a curved path the tangent of which is 4545 in relation to such plane, and will advance about 5.71 along a circle in the stated reference plane, in each revolution of the assembly. With two nozzles as shown, the respective paths will be separated by 2.855. Also, inasmuch as two nozzles are employed, in any series of sucoessive travel paths, one will be in a downward direction and one in an upward direction. All paths in the same direction will be parallel, and with those extending generally upward intersecting those extending generally downward substantially to form a criss-cross or checkboard pattern over any given wall surface.

The path relationships preferred have been stated; others may be attained by varying the hunting tooth ratio, i.e. a tooth relationship of 62 to 64 between the nozzle and assembly gears 121 and 76 respectively would result in a different degree advance of each path, namely 5.8064 (360-2-62). If the ratio were 65 teeth in the nozzle gear to 64 in the assembly gear, the advance would be 5.6923. After one cycle, or a number of revolutions about the longitudinal axis of the assembly which is equal to the number of teeth in the nozzle gear 121, the paths repeat themselves. As may be noted, the

7 degree of advance decreases with an increase in the number of teeth in the nozzle gear 121, and the number of paths described increases.

The rate at which the cycle is accomplished depends entirely upon tihe braking action imposed by the degree of restriction of the discharge ports of the pump contained within the case 1. Where intensive contact action is required, the restriction is increased and thereby thespeed of rotation is reduced, enabling the streams to pass over the wall surfaces more slowly. Ordinarily, the ratio between nozzle gear 121 and assembly gear 76 is preferred to be 63:6'41' More intensive or lessintensive contact is attained by varying the speed of rotation by means of the pump orifice dimensions. If more than two nozzles are employed in the nozzle structure, the pattern described will not change substantially, but the formed paths will be closer together.

While the apparatus according to the present invention has been exemplified by a showing wherein a recipro 13 What is claimed is: 1. In an apparatus for applying liquid streams against the interior surfaces of a walled enclosure, wherein said apparatus includes a liquid supply and support tube,

adapted for flow connection to a liquid supply conduit; a liquid delivery head, defining an internal passageway, mounted on said tube for rotation about the axis there of, with said internal passageway in communication at one end with said tube; and a hollow nozzle structure, adapted to be mounted on said head for rotation about a second axis perpendicular to said tube axis, and in communication with said head defined passageway at the other end thereof; means for rotating said nozzle structure and said head about said respective axes, comprising at least two jet reaction, discharge nozzle elements in said nozzle structure disposed in substantially coplanar, radially oifset, and angularly opposed discharge relation; a first ring gear engageable in fixed coaxial relation with said nozzle structure; a second ring gear mounted on said support tube for fixed coaxial relation thereto; a gear case mounted in separably dependent relation to said delivery head, said case adapted to contain a body of a liquid lubricant; a drive connection between said first and second ring gears, including a first shaft journalled in said case in substantially parallel relation to said second axis; a second shaft journalled in said case; a governor pump, adapted to control the speed of rotation of said nozzle structure about said second axis, and thereby the speed of rotation of said delivery head about said first axis, disposed and supported within said gear case, said pump including a pump casing, a pump chamber defined within said casing, and inlet and outlet orifice means defined by said casing to communicate between said chamber :and the interior of said gear case; a drive connection between said pump and said second shaft; and a drive connection between said first and second shafts.

2. An apparatus according to claim 1, wherein said inlet and outlet orifice means defined by said pump casing, comprises at least one passageway having an inner end opening into said chamber and an outer end opening into siad gear case, and valve means supported in said casing for reciprocal movement in said passageway to vary the flow area thereof.

3. An apparatus according to claim 1, wherein said governor pump comprises a positive displacement pump.

4. An apparatus according to claim 3, wherein said positive displacement pump comprises a vane pump.

5. An apparatus according to claim 3, wherein said positive displacement pump comprises a reciprocating pump.

6. In an apparatus for applying liquid streams against the interior surfaces of a walled enclosure, wherein said apparatus includes: a support and liquid supply tube, adapted for flow connection to a liquid supply conduit; a liquid delivery head defining aninternal passageway, mounted on said support tube for rotation about a first axis longitudinally of said supply tube, with said passageway in communication at one end thereof with said liquid supply tube; and a hollow nozzle structure, adapted to be mounted on said delivery head for rotation about a second axis perpendicular to said tube axis, and in communicating flow relation to the other end of said delivery head passageway; means for rotating said nozzle structure and said liquid delivery head about said respective second and first axes, comprising at least two jet reaction, discharge nozzle elements in said nozzle structure disposed in substantially co-planar, radially ofiset, and angularly opposed discharge relation; a first ring gear engageable in fixed coaxial relation with said nozzle structure; a

second ring gear mounted on said support tube for fixed coaxial relation thereto; a gear case mounted in separable, dependent relation to said delivery head, said case adapted to contain a body of a hydraulic liquid and lubricant; a drive connection between said first and second ring gears, including a first drive shaft journalled in said case in substantially parallel relation to said second axis; a second shaft journalled in said case; a governor pump adapted to control the speed of rotation of said nozzle structure about said second axis, and thereby the speed of rotation of said delivery head about said first axis, including a pump cylinder disposed within said gear case, said cylinder having a closed end and an open end; means for mounting said cylinder closed end in said gear case for pivoted oscillatory movement of said cylinder; a piston head fitted in said cylinder for reciprocal movement longitudinally thereof and defining a pump chamber with said cylinder closed end; a piston rod having an inner end in rigid relation to said piston head, and an outer end extended outwardly through the open end of said cylinder; a crank engageable between said second shaft and said piston rod; orifice means formed by at least one passageway defined in said cylinder closed end for communication between said gear case and said pump chamber; and a drive connection between said first and second shafts.

7. In an apparatus for applying liquid stream against the interior surfaces of a walled enclosure, wherein said apparatus includes: a support and liquid supply tube, adapted for flow connection to a liquid supply conduit; a liquid delivery head, defining an internal passageway, mounted on said support tube for rotation about a first axis longitudinally of said supply tube, with said passageway in communication at one end thereof with said liquid supply tube; and a hollow nozzle structure, adapted to be mounted on said delivery head for rotation about a second axis perpendicular to said tube axis, and in communicating flow relation to the other end of said delivery head passageway; means for rotating said nozzle structure and said liquid delivery head about said respective second and first axes, comprising at least two jet reaction, discharge nozzle elements in said nozzle structure disposed in substantially co-planar, radially offset, and angularly opposed discharge relation; a first ring gear engageable in fixed coaxial relation with said nozzle structure; a second ring gear mounted on said support tube for fixed coaxial relation thereto; a gear case mounted in separable, dependent relation to said delivery head, said case adapted to contain a body of a hydraulic liquid and lubricant; a drive connection between said first and second ring gears, including a first drive shaft journalled in said case in substantially parallel relation to said second axis; a second shaft journalled in said case; a governor pump adapted to control the speed of rotation of said nozzle structure about said second axis, and thereby the speed of rotation of said delivery head about said first axis, including a pump casing mounted within said gear case in fixed relation thereto, said casing providing a pump chamber and an internal bearing for one end of said second shaft, a vane pump impeller in said chamber and on said shaft; orifice means including at least one set of inlet and outlet passageways defined in said pump casing to communicate between said pump chamber and the interior of said gear case; and a drive connection between said first and second shafts.

References Cited in the file of this patent UNITED STATES PATENTS 2,120,784 Howold June 14, 1938 2,714,080 Kennedy et a1 July 26, 1955 2,766,065 Joyslen Oct. 9, 1956 

